Pump



Oct. 14, 1930. l. H. WILSEY 1,778238 PUMP Fileci Jan. 11, 1926 3 Sheets-Sheet 1 Oct. 14, 1930. I. H.WILSEY 1778,238

PUMP

Filed Jan. 11, 1926 3 Sheetsheet 2 I. H. WILSEY Oct. 14, 1930.

PUMP

(5 Sheet's-Sheet 3 Filed Jan. 11, 1926 Patented Oct. 14, 1930 UNITED STATES PATENT OFFICE IRVEN' E. WILSEY, 01 CHICAGO, ILLINOIS, ASSIGNOR T JAMES B. T'U'THEL, O1

CHICAGO, ILLINOIS PUMP Applicaitlon flled Jani1ary 11, 1926. Serial N0. 80,435.

The inventionrelates to improvements in rotary umps for transmitting oil und other liquids.

A eneral object of the invention is' to 5 provie a new and improved pump which is adjustable to va1y and reverse the flow of liquid, und which serves to meter the flow 0f liquid.

Another object is to provide a pump of the above character hzwing no valves, such as check valves, thereby requiring power only t0 pump the oil, und furt-hermore preventing the fiashing of volatile liquicl on the suction stroke due to the added partial vacuum necessar to overcome ordinary valve resistance.

n many pri0r rotary pumps having reciprocatory plungers, the outer ends 0f the cylinders open directly into the inlet and exhaust chambers so tl1at when tl1e pump is operated at a high speed centrifugal force Will cause Y partial evacuation of the cylinders 011 the suction stroke, thereby lowering the elfective capacity of the pump and limiting the speecl ab which it can be successfully operated. An

important object of the present invention is to provide a pump which can operate at a high speed withouc such evacuation, und in which centrifugal force Will cause pressure on the piston heads during the suction stroke thereby causing the pump t0 operate als maximum capa city.

Other importanc objects 1eside in the provision of a rotary pump which even though 0f a large size and operating at a high speed has a 10W rubbing velocity als the valve ports, which has a relatively small area of friction surfaces nt any place, and in which all principal thrusts are taken up by ball or roller bearings revolving ab proper speeds irrespective f the speed 0f the pump.

Another object is 130 provide a pump which when conveying volatile liquide: Will not leak liquid or vapor into the surrounding air, and in which liquid seals are provided to prevent air from being drawn into tl1e cylinders 011 the suction stroke.

Still other objects cf the invention are to taper the ports and theends 0f the pistons so as to elimi nate air und vacuum pockets and consequently to prevent hammer; in which all centrifugal forces in the pistons are balancecl; in which side pressure between tl1e pistons and cylinders is reduced, thereby minimizing wear, retaining a lubricating film und preventing noise; and in which leakage past Ehe pistons is utilizecl t0 lubricate other purts of the pump und to lubricate such parts in direct proportion t0 ehe work being doue.

A further object is to provide a novel pump which is simple and inexpensive in construction, which is eflicient in operation over a wide range particularly at partial loads since no part of the liquid is by-passed, und which can be used as an engine.

Further objects and advantages will become apparent as the description proceeds.

Figure 1 is a vertical sectional view of a pump emboclying the features of my invention.

Fig. 2 is a fIOII'G end view thereof.

F ig. 3 is a sectiona1 view taken along line 33 0f Figure 1.

F ig. 4 is a sectional view of the valve coustruction taken along line 41 of Figure 1.

Fig. 5 is a seetionul view of the valve coustruction taken along line 55 of Figure 1.

Fig. 6 is a detail sectional view taken along line 66 of Figure 1.

VVhile the invention is susceptible of various modifications und alternative constructions. I h2we shown in the drawings anal Will herein clescribe in cletail the preferred embodiment, but it is t0 be understood that I do not thereby intencl t0 limit the invention to the specific form disclosed but aim o cover all modifications anal alternative constructions falling within the spirit und scope of the invention as expressed in the appended claims. Referring more particularly t0 the drnwings, the pump comprises -a suitable casins: 10 a. roter 11 mounted in the casing und having a plurality of cylinder ar1d piston units, and means preferably a pin 12 adjustably mounted in the casing and serving to control the actions of the pistons.

The casing 10 preferably is cylindrical in form, and is closed ab one end by a ribbed Wall 13. A cover 14 is removablv secured to the other end 0:E the casi'ng by bolts 15, and is formed with strengthning ribs 16. Formed at spaced points on the peripheral Wall of the casing are a plurality of stands 17 for supportin the pump on a suitable support (not shown%.

Oentrally formed on the outside of the Wall 13 and opening therethrough is an elongated bearing and valve casing 18 having a conical valve seat 19. The outer end of the casing 18 is closed by an end cap 20 provided with a suitable stufling box 21. Formed on one end 01: the rotor 11 is an enlogated tapered hub 22 which fits closely against the valve seat 19, and the outer end of which is reduced in size as indicated at 23. The hub 22 is rotatably mounted at its ends in suitable ball bearings 24 and 25, 0f which the bearing 24 is positioned in an annular space 26 formed in the inner end of the casing 18. The bearing 25 is a partial thrust bearing, and is positioned on the reduced end 23 013 the hub and in an annular notch 27 cut in the outer end 0f the casing 18. Extending through the hub 22 to which it is rigidly secured by a key 28 is a drive shaft 29 which extends outwarly through the stuffing box 21 for connection with a suitable sourceof power (not shown). The hub 22 is held against the seat 19 by :a pair of lock nuts 30 turned onto a threaded section 31 of the shaft 29 in a chamber 32 foimed in the end cap 20, and engaging the outer end of the bearing 25. Wear on the hub 22 0x seat 19 can be taken up by adjusb ing the nuts 30, a space being left between the end of the hub and the bearing 25 to permit this adjustment. By eupporting the roter 11 through the hub 22, the former can be driven at an extremely high speed without subjecting the bearings to an excessive speed, and the friction areas are relatively small, thereby permitting efiicient operation with minimum wear and loss of power through friction.

A plurality of cylinders, four cylinders 33, 33", 33, and 33 in the present instance, are formed at the periphery of the rotor 11. These cylinders are radial, a1'e spaced 90 apart, and the diametrically opposed cylinders are in alinment. F01 ease in assembling, the cylinders are split, outer semicylindrical ca ps 34, 34 34, and 34 being secured by bolts 35 to semi-cylindrical brackets 36, 36", 36, and 36 on the rotor 11. The outer ends 0f the cylinders are closed by end caps 37, 37", 37, and 37 secured thereto 55 by bolts 38. The inner ends of the cylinders are open to the atmosphere.

The outer ends of the cylinders are respectively connected by pressure fluid passa zes 39, 39", 39, and 39, extending' inwardly through the brackets 36, 36", 36, and 36 and longitudinally through the hub 22, Witlu valve ports 40, 40", 40, and '40 in the peripheral surface of the hub ne xt to the valve seat 19. Each valve port is located in the same plane and on the same sideof the rotor 11 as the cylinder with whicl1 it is connected. Surrounding the hub 22 at the valve ports is a valve chamber 41 formed in the casing 18, and divided into two parts by two diametrically opposed lands 42 and 43. Opposite sides of the chamber 41 open respectively into passages 44 and 45 which are adapted to be connected 130 suitable fittings (not shown) adapted to be attached t0 the casing 18 by flanges 46. Fluid may be admitted through one of the passages 44 and 45, and discharged through the other, the specific direction of flow depending upon the action 0f the pump. It Will be evident that the hub 22 constitutes a valve which upon' rotation of the rotor will successively and alternately connect the opposed cylinders t0 opposite sides 015 the chamber 41. By being located near the axis of rotation, the valve surfaces have a 10W rubbing velocity, thereby permittinga high pump speed without limiting the latter.

T0 minimize leakage of fluid 01' ai1 past the bearing surfaces between the ball bearing 25 and the valve ports, an annular plate 47 is positioned against the inside of the ball bearing, and an annular ring 48 is mounted in a notch 49 in the'outer end surface of the hub 22 next to the plate. A plurality of coil springs 50 positioned in bores 51 opening into the notch 49 press the ring 48 against the plate 47. Fluid Will be trapped by the ring 48 in the space 52 between the outer end of the hub 22 and the plate 47, and Will seal the space between the hub and the seat 19. The small amount of fluid that may pass through to the chamber 32 may be drained away through an opening 53 adapted to be counected to a fiuid return pipe (not shown). T0 prevent leakage between the ball bearing 24 and the chambe'r 41, an annular notch 54 is cut in the inner end of the housing 18 next to the inner raceway of the ball bearing, and an annular ring 55 is*positioned in a groove 56 cut in the side of the notch. The ring 55 is pressed into engagement With the inner raceway of tl1e ball bearing 24 by a plurality of springe 57 located in bores 58 opening into the groove 56. Fluid trapped by the 1'ing 55 in the groove 54 next to the hub 22 Will seal the space between the ball bearing 24 and the chamber 41. Any fluid that may collect in the housing 10 may be drained away through an opening 59 adapted to be connected t0 a suitable return pipe (not shown). By minimizing leakage, the efllciency 0f the pump is materially increased. 1

Mounted in the cylinders 33, 33", 33, and 33, are pistons 60, 60", 60 and 60 respectively. Each piston has a core 61 in its end, the outer end of wich is slightly ointed t0 avoid hammer. The opposed cylin ers 60 and 60, and 60" and 60 are rigidly connected by rectangular yokes 62 and 63 respectively. These yokes are ofi"set in opposite diinders.

rections from the centers of the pistons, and are movable at rigl1t angles to eaclx othor in a space 64 in the center of tlle rotor 11.

The relative movement of' the pistons in the cylinders is controlled by the pin 65 whiclx is secured in ball bearings 66 and 67 mounted in turn in blocks 68 and 69 slidably disposed in the okes 62 and 63 respectively. By providing tlle yoke and block construction, an axial thrust over a substantial area is applied to the pistons, thereby eliminating lateral forces and obtaining a reduced pressure between tl1e sides of the pistons and cyl- As a result, power losses due to frietion are reduced, and a lubricant having a 10W resistance 130 pressure may be used.

T0 minimize leakage from the cylinders past the p-istons, peripheral groo'ves 70 are c1'1t in the pistons, one groove for each piston, and these grooves are connected by passage 71 extending longitudinally through the pistons t0 the bearing surfaces between the yokes 62 and 63, and the blocks 66 and 67 Fluid passing to the grooves 70 is trapped there, and part thereof is used to lubricate the bearing surfaces just referred to. The amount of lubrication will be directly proportional to the work performed by the pu'mp. T0 further minimize leakage the inner edges of the pistons are chamfered at 7 2, and the inner peripheral edges of the cylinders are formed with notches 73. Due to centrifugal force any fluid leaking past the pistons will be held in the ohamfered spaces 72 and in the notches 73. Any fluid falling into the casing 10 can be drained away through the outlet 59. By minimizing leakage, power losses are reduced, the.pump capacity is increased, and the efficiency is in general increased. Elimination of leakage is particularly important where volatile oils are being pumped, as in oil refineries, for such volatile oils, ifleaking 110 the atmosphere, may ignite.

If the pin 65 is concentrio with the shaft 29, no movement of the pistons will result upon rotation of the roter 11. If the pin 65 is eccentric to the shaft 29 then movement will result with a consequent pumping action. Anysuitable means for adjustably supporting the pin 65 may be provided. In the present instance, the pin is mounted in an adjustable block 74 disposed in opening 75 in the center of the cover 14. The opening is surrounded by a flange 76. The block has upper and lower guide pins 77 and 78 two o.f each, which extend slidably through earings 79 formed in the upper and lower sides of the fiange 76. Mounted 0n the outer end of the pin65 is a block 80 which is adjustably disposed in a yoke 81 formed on the short arm of a bell crank lever 82. The latter is mounted on a pivot 83 011 the cover 14, and the long arm has a handle 84 for adjusting the pin 65. The handle 84 is adapted to be clamped in adjusted Position, when a comstant flow is desired, by means of a wing nut 85 thereon engaging a holt 86 which is slidable in a slotted arcuate member 87 0n the cover. The pin thus is adjustable in a straight line across the axis of the shaft 29.

flo cause each piston for any two opposed .ports to be at the end of its stroke when the ports are cut ofi by the lands 42 and 43, this line of movement must be in the plane of the lands.

The pin 65 is easily adjustable since when any two ports are cut ofi by the lands, free end movement of the corresponding pistons is permitted. The only force 0n the pistons at that time is lateraland the resistance presented by the fluid trapped in the end of one piston is counterbalanced by the thrust of the other pair of pistons. When all the ports are open, the thrusts of the pistons are opposed, thereby still avoiding resistance to the adj ustment of the pin 65.

In operation, when the pin 65 is in line with the shaft 29 no pumping action results, the pistons remaining stationary in the cylinders and rotating on tl1e ball bearings 66 and 67. Assuming that the shaft 29 is rotating in a clockwise direction, as the pin 65 is adjusted into a position above the shaft 29, as shown in Figure l, fluid will be drawn in through the assage 45 and discharged.

through the passage 44. Upon rotation of the rotor, one of each pair of pistons moves inwardly as its port moves across the passage 45, therebycreating a suction, and the other piston moves outwardly as its port crosses the passage 44, thereby expelling the fluid in its cylinder. When the two pistons of a pair are in a vertical position as shown in Figure 1, all the fluid in the upper cylinder has been expelled and the lower cylinder has been filled. Due to the radial direc tion of the passages 39 (a to d) in the brackets 36 (a to d) a centrifugal force resulting from the rotation of the rotor tends to fil] the ends of the cylinders. This results in increasing the efliciency of the pump since no waste of space in the cylinders obtains. As the pin 65 is adjusted into a position below the shaft 29, the directional flow of the fluid will be reversed, i. e. fluid will be admitted through passaae 44 and discharged through passage 45. The rotation of the shaft however will continue in the same direction. The extent of reciprocation of the pistons and hence the volume of the flow of liquid is deter mined by the degree of eccentricities of tl1e pin 65 to the shaft 29. It will be seen that by this construction a very fine control of the flow in volume and direction is available.

It Will be seen that I. have provided a simple and inexpensive pump which can be easily assembled, easily repaired, and which is extrernely eflicient in operation. A minimum loss of ower due to friction and leakage results, and therefore the maximum capacity i'saVailable. The pump de to the prevention of excessive leakage is particularly adapted for use where volatile 0il is to be transmitted. All the lot-ative parts are mounted in ball bearings. Tl1e ball bearings are subjected to relatively 10W speeds of rotation. This is also true of the valve Surfaces. Because of the low resistance lue to the small bearing surfaces which are requirecl the pump can be easily stanted, particularly if the pin is moved intg central Position so that no power need be expended in actual pumping. Perfect control of the flow without the use 0f by-pass valves is provided, thereby utilizing all of the power in the actual transmission of fluid.

I claim as my invention:

1. A pump having, in combination, a casing having a bearing member in one end thereof, said bearing member being formed with a valve chamber, lands dividing said chamber into two parts, a rotor having a hub rotatably mountedin said bearing. said rot0r having a plurality 0f cylinders at its periphery, a plurality of passages extending substantially radially an(l inwardly from the outer ends of said cylinders through the end Wall of said rotor and lengthwise 0f said hub, and terminating in orts in the peripheral surface of the l1ub, said ports being adapted 130 be moved successively into communication with opposite sides of said valve chamber, a plurality 0f pistons one mounted in each cylinder, and means operative to reciprocate said pistons in said cylinders upon rotation of said roter.

2. A pump having, in combination, a casing having a bearing member in one end thereof, said bearing member beim; formed with a valve chamber, lands dividing said chamber into two parke; a rotor having a hub rotatably mounted in said bearing, said roter having a plurality 0f cylinders at lts periphery, a plurality of passages extenrling substantially radially and inwardly from the outer ends of said cylinders through the end Wall of said rotor ancl then lengthwise 0f said hub, and terminatinb; in ports in the peripheral surface of the hub, said ports being adafltecl to be moved successively into communication With opposite sides of said valve chamber a plurality of pistons, one mounted in each cylinder, .and

means operative t0 reciprocate said nistons in said cylinders upon rotation of said roter, said means being adjustable across the axis 0f rotation t0 reverse the flow of fluid and to vary the a'mount of flow in either (lirection.

3. A pump having, in combination a valve casing bearings in opposite ends of said valve casing, said valve casing having a valve ehamber therein, lands dividing said chamber into two oppbsed partsa rotor having a.hub rotatably mounted in said bear-.

means being adjustable in an axial plane through said lands into and out 0f eccentricity with the axis of rotation.

4 A pump having, in combination, a casing, a rotor journaled in said casing and having a plurality of radial cylinders, said cylinders being arranged in pairs of diametrically opposed cylinders, pistons slidably mounted in said cylinders, opposed pistons being connected by a lateral yoke, a pluralit v 0f sliding blocks, one mounted in each yoke, a pin rotatably engaging said blocksfor movement therewith, said pin being mounted in said casing for adjustment into eccentric relation with the axis of rotation, and valve means for admitting: and discharg1'ng fluid t0 and from said cylinders in timed relation to the reciprocation 0f said pistons.

5. A pump having. in comb ination, a casing, a rotor mountecl in said casing and having a pluralitv of cylinclers ab its periphery, a plurality 0f pistons. one in each cylinder, the outer ends of said pisfons beim: tapered t0 reduce hammer, means eccentric t0 the axis of rotation engasjng saicl pistons to cause reciprocation 0f the latter upon 1'0- tation of sai l rotor, and means for admitting fluid to and from said cyl inclers. 1

6. A pump havinsz. in combination, a bearin g. a rotor mounted in said bearing and havingr a pluralitv cf c vlinders at its periphery', a plurality of pistons, one in each cylinder, means engaging the inner ends 0f said pistons, said means beinq capable of being posi tioned in eccentric relation to the axis of rotation to cause reciprocation of said pistons in said cylinclers, and a plurality of passages, one in each piston extencling from the inner surface 0f the associated cylinder inwardly to the b'earing surfaces between said piston ancl said means said passage serving 130 direct fluid leakin,q partially past said piston to said bearing surf'aces 130 lubricate the latter in direct proportion to the work done by said pump. and means for admitting and discharging fluid to and from said cylinders.

7. A pump havingqin combination, a casing. a roter mounted in said casing, said rotor having a plurality of radial cylinders closed ab their outer ends, a plurality 0f pistons, one in eacl1. cylinder, means between the inner ends 0f said cylin'ders, said means engaging said pistons and being adapted to be moved into eccentric relation to the axis of rotatiori to cause reciprocation of said pistons, notches formed in the inner ends of said cylinders and the heads of said pistons, said not'ches being adapted t0 be fi1led With fluid leaking past said pistons to minimize said leakage, and valve means-for directing pressure fluid to and from the outer ends of said cylinders.

8. A pump having, in combination, a valve casing having a valve chamber and a, valve seat, 1ands dividing said chamber into two parts, a roter having a hub engaging said seat, said hub having Ports adapted to be moved across said lands am]. successively into communication with opposite sides of said chamber, piston and cylinder units on said roter, means f0r actuating said pistons in said cylinders upon rotation o:f said roter, said rotor having passag'ges, one connecting each cylinder With one 0f said ports, and means confining a small space at each end 015 said seat to seal the spacesbetween said seat and said hub at .opposite sides of said chamber.

9. A pump havin in combination, a va1ve casing having a va ve chamber and a valve seat, lands dividing said chamber into two parts, a rotor hawing a hub engaging said seat, said hub having ports adapted to be moved across said lands and successively into comrnunication with opposite sides of' said chamber, piston and cylinder units on said rotor, means for actuating said pistons in said cylinders upon rotation of said roter, said rotor haVing passages, one connecting .each cylinder with one of said ports, and

means f'01 sealing the space between said seat and said hub at one side of said chamber to reduce the leakage of fluid therethrough.

10. A pump having, in combination, a bearing; a rotor journaled in said bearing and having a plurality 0f cylinders exfending toward the periphery thereof, a plurality of pistons, one mounted in each cylinder, block slidably adjustabl'e in oneend 0f said casing, a pin in said block, said pin engaging said pistons and when located eccentric'ally of the axis of rotation serving t0 cause reciprocation' of said pistons in said c linders, valve means for directing p1essure uid to und from said cylinders, and means for adjusting said block in a Plane passing through the axis 0f rotation.

11. A pump having, in combination, a combined bearing und valve member having a conical seat und a vp.1ve chamber openmg through opposite sides of said 'seat, a rotor having a conical hub engaging said saut und. having a plurality of orts opening through its peripheral surface 0 r movement into successive communication with opposite sides of said valve chamber, means for adjusting said hub axially in said member to take u wear 01 looseness, a plurlity of pistoh an cylinder units in said roter, and pass ages connect- 

